CA2303100C - Plunger seal assembly for a high pressure pump - Google Patents
Plunger seal assembly for a high pressure pump Download PDFInfo
- Publication number
- CA2303100C CA2303100C CA002303100A CA2303100A CA2303100C CA 2303100 C CA2303100 C CA 2303100C CA 002303100 A CA002303100 A CA 002303100A CA 2303100 A CA2303100 A CA 2303100A CA 2303100 C CA2303100 C CA 2303100C
- Authority
- CA
- Canada
- Prior art keywords
- seal
- annular
- plunger
- bore
- annular groove
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000012530 fluid Substances 0.000 claims abstract description 13
- 239000000463 material Substances 0.000 claims abstract description 6
- 238000003754 machining Methods 0.000 claims abstract description 5
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 2
- 239000004699 Ultra-high molecular weight polyethylene Substances 0.000 claims description 2
- 239000000919 ceramic Substances 0.000 claims description 2
- 229910002804 graphite Inorganic materials 0.000 claims description 2
- 239000010439 graphite Substances 0.000 claims description 2
- 229910002077 partially stabilized zirconia Inorganic materials 0.000 claims description 2
- 239000011347 resin Substances 0.000 claims description 2
- 229920005989 resin Polymers 0.000 claims description 2
- 229920000785 ultra high molecular weight polyethylene Polymers 0.000 claims description 2
- 238000000034 method Methods 0.000 claims 1
- 238000010438 heat treatment Methods 0.000 abstract description 4
- 238000004519 manufacturing process Methods 0.000 abstract description 2
- 238000001125 extrusion Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
- F04B53/164—Stoffing boxes
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Sealing Devices (AREA)
- Compressor (AREA)
- Sealing With Elastic Sealing Lips (AREA)
Abstract
A high pressure fluid seal assembly is shown and described. The seal assembly includes a seal carrier having a bore through which a reciprocating pump plunger may pass, the seal carrier having a first annular groove concentric with the bore, and carrying an annular seal. The seal carrier further includes an integral annular guidance bearing positioned in a second annular groove of the seal carrier, the second annular groove and guidance bearing contained therein being axially spaced from the first annular groove and seal contained therein. An inner diameter of the guidance bearing is smaller than an inner diameter of the seal carrier in a region between the seal and the guidance bearing. The seal is therefore supported directly by the seal carrier, although the seal carrier is spaced from the reciprocating plunger by the guidance bearing. Frictional heating in the region of the seal is therefore reduced, thereby increasing the life of the seal. Materials for the plunger, seal and guidance bearing are selected to minimize friction between the plunger and seal and between the plunger and guidance bearing. Furthermore, the seal assembly is manufactured by pressing the guidance bearing into the seal carrier, and then machining the bore in the guidance bearing and in the seal carrier in the same setup, thereby improving the alignment of the elements and simplifying manufacturing.
Description
PLUNGER SEAL ASSEMBLY FOR A HIGH PRESSURE PUMP
TECHNICAL FIELD
This invention relates to high pressure seals, and more particularly, to high pressure fluid seals for pumps having reciprocating plungers.
BACKGROUND OF THE INVENTION
In high pressure fluid pumps having reciprocating plungers, it is necessary to provide a seal around the plunger to prevent the leakage of high pressure fluid. In such pumps, the seal must be able to operate in a high pressure environment, withstanding pressures in excess of 10,000 psi, and even up to and beyond 50,000-70,000 psi.
Currently available seal designs for use in such an environment include an extrusion resistant seal supported by a back-up ring, the back-up ring and seal being held by a seal carrier. However, the tolerances for clearance between the plunger and back-up ring are very difficult to achieve and maintain. Very typically, therefore, the plunger and back-up ring come into contact, generating frictional heating, which in turn causes the seal to fail.
Accordingly, there is a need in the art for an improved high pressure fluid seal assembly, and in particular, a seal assembly that is simple to manufacture accurately, and that will increase the life of the seal. The present invention fulfills these needs, and provides further related advantages.
SUMMARY OF THE INVENTION
Briefly, the present invention provides an improved high pressure fluid seal assembly for use in a high pressure pump having a reciprocating plunger.
In a preferred embodiment, the seal assembly includes a seal carrier having a bore through which the reciprocating plunger passes. The seal carrier has a first annular groove that is concentric with the bore and that carries an annular seal, an end region of the seal being supported by the seal Garner. The seal carrier has an integral annular guidance bearing that is positioned in a second annular groove of the seal carrier, the second annular groove and guidance bearing contained therein being concentric with the bore and being axially spaced from the first annular groove and seal. The bore through the seal carrier is therefore defined by an internal circumference of the guidance bearing, an internal circumference of the seal, and an inner region of the seal carrier positioned between the seal and the guidance bearing. An inner diameter of the guidance bearing is smaller than the inner diameter of the bore of the seal carrier in the region between the seal and the guidance bearing, thereby preventing the plunger from contacting the seal carrier. In this manner, the seal is supported by the seal carrier, and the seal carrier is separated from the plunger by the guidance bearing, thereby reducing frictional heating and extending the life of the seal. Also, the materials for the guidance bearing and plunger are selected to minimize the friction between the two elements.
The guidance bearing is positioned in the seal carrier, and the bore is then machined in the seal carrier and in the guidance bearing in the same setup, thereby improving the concentricity and alignment of the guidance bearing and portion of the seal carrier that supports the annular seal.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a cross-sectional plan view of a pump assembly incorporating a seal assembly provided in accordance with a preferred embodiment of the present invention.
Figure 2 is an enlarged cross-sectional plan view of the seal assembly illustrated in Figure 1.
Figure 3 is a cross-sectional plan view of an element of the seal assembly illustrated in Figures 1 and 2.
DETAILED DESCRIPTION OF THE INVENTION
An improved high pressure fluid seal assembly 10 is provided in accordance with a preferred embodiment of the present invention, as illustrated in Figure 1. The seal assembly 10 is for use in a high pressure pump assembly 22 having a reciprocating plunger 14 coupled to a drive mechanism 26. The plunger 14 reciprocates in a high pressure cylinder 24, the seal assembly 10 preventing the leakage of high pressure fluid from a high pressure region 23 within the high pressure cylinder 24.
TECHNICAL FIELD
This invention relates to high pressure seals, and more particularly, to high pressure fluid seals for pumps having reciprocating plungers.
BACKGROUND OF THE INVENTION
In high pressure fluid pumps having reciprocating plungers, it is necessary to provide a seal around the plunger to prevent the leakage of high pressure fluid. In such pumps, the seal must be able to operate in a high pressure environment, withstanding pressures in excess of 10,000 psi, and even up to and beyond 50,000-70,000 psi.
Currently available seal designs for use in such an environment include an extrusion resistant seal supported by a back-up ring, the back-up ring and seal being held by a seal carrier. However, the tolerances for clearance between the plunger and back-up ring are very difficult to achieve and maintain. Very typically, therefore, the plunger and back-up ring come into contact, generating frictional heating, which in turn causes the seal to fail.
Accordingly, there is a need in the art for an improved high pressure fluid seal assembly, and in particular, a seal assembly that is simple to manufacture accurately, and that will increase the life of the seal. The present invention fulfills these needs, and provides further related advantages.
SUMMARY OF THE INVENTION
Briefly, the present invention provides an improved high pressure fluid seal assembly for use in a high pressure pump having a reciprocating plunger.
In a preferred embodiment, the seal assembly includes a seal carrier having a bore through which the reciprocating plunger passes. The seal carrier has a first annular groove that is concentric with the bore and that carries an annular seal, an end region of the seal being supported by the seal Garner. The seal carrier has an integral annular guidance bearing that is positioned in a second annular groove of the seal carrier, the second annular groove and guidance bearing contained therein being concentric with the bore and being axially spaced from the first annular groove and seal. The bore through the seal carrier is therefore defined by an internal circumference of the guidance bearing, an internal circumference of the seal, and an inner region of the seal carrier positioned between the seal and the guidance bearing. An inner diameter of the guidance bearing is smaller than the inner diameter of the bore of the seal carrier in the region between the seal and the guidance bearing, thereby preventing the plunger from contacting the seal carrier. In this manner, the seal is supported by the seal carrier, and the seal carrier is separated from the plunger by the guidance bearing, thereby reducing frictional heating and extending the life of the seal. Also, the materials for the guidance bearing and plunger are selected to minimize the friction between the two elements.
The guidance bearing is positioned in the seal carrier, and the bore is then machined in the seal carrier and in the guidance bearing in the same setup, thereby improving the concentricity and alignment of the guidance bearing and portion of the seal carrier that supports the annular seal.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a cross-sectional plan view of a pump assembly incorporating a seal assembly provided in accordance with a preferred embodiment of the present invention.
Figure 2 is an enlarged cross-sectional plan view of the seal assembly illustrated in Figure 1.
Figure 3 is a cross-sectional plan view of an element of the seal assembly illustrated in Figures 1 and 2.
DETAILED DESCRIPTION OF THE INVENTION
An improved high pressure fluid seal assembly 10 is provided in accordance with a preferred embodiment of the present invention, as illustrated in Figure 1. The seal assembly 10 is for use in a high pressure pump assembly 22 having a reciprocating plunger 14 coupled to a drive mechanism 26. The plunger 14 reciprocates in a high pressure cylinder 24, the seal assembly 10 preventing the leakage of high pressure fluid from a high pressure region 23 within the high pressure cylinder 24.
More particularly, as illustrated in Figures 2 and 3, the seal assembly 10 includes a seal carrier 12 having a bore 13 through which the reciprocating plunger 14 passes. The seal carrier 12 has a first annular groove 15 in which an annular seal 17 is positioned. An annular elastomeric seal 25 is provided around the outer circumference of annular seal 17, to energize the annular seal 17 during the start of a pressure stroke.
A bushing 50 positioned within the high pressure region 23 houses a spring 52 which engages the annular seal 17 and urges it toward the first annular groove 15 to substantially prevent the annular seal from moving out of the first annular groove. The annular seal 17 has a flange portion 54 which engages the spring 52 and substantially prevents the spring from moving laterally into contact with the plunger 14.
The seal carrier 12 also has an integral, annular guidance bearing 19, which is positioned in a second annular groove 16 within the bore 13. As seen in Figure 3, the second annular groove 16 and guidance bearing 19 positioned therein are axially spaced from the first annular groove 15 and annular seal 17 contained therein.
The inner diameter 20 of the guidance bearing 19 is smaller than the inner diameter 21 of the seal carrier bore 13 in a region 11 between the seal 17 and guidance bearing 19. For example, in a preferred embodiment, the inner diameter 20 is .0005-.0015 inch smaller than the inner diameter 21. In this manner, the end region 18 of annular seal 17 is supported by region 11 of the seal carrier 12; however, region 11 of seal carrier 12 is not in contact with the plunger 14, given the configuration of the guidance bearing 19.
A seal assembly provided in accordance with a preferred embodiment of the present invention therefore supports a seal directly by the seal carrier, eliminating the need for a back-up ring. The integral guidance bearing prevents the plunger from contacting the seal carrier, thereby reducing the frictional heating in the vicinity of the seal, which in turn extends the life of the seal. To further increase the longevity of the assembly, the materials for the components are selected to minimize the friction between the plunger and the guidance bearing and between the plunger and the seal. In a preferred embodiment, the plunger 14 is made of partially stabilized zirconia ceramic, the guidance bearing 19 is made of a resin impregnated graphite, and the seal 17 is made of an ultra-high molecular weight polyethylene. However, it should be noted that a variety of materials may be used, and the selection of the materials for the components are interdependent.
To further increase the reliability of the seal, the seal assembly is preferably manufactured by pressing the guidance bearing 19 into the seal carrier 12, and machining the bore through the guidance bearing and through region 11 of the seal carrier in the same machining setup. As discussed above, the inner diameter of the bore in region 11 is machined slightly larger than the inner diameter 20 of the bore through the guidance bearing. However, by machining both areas in the same setup, the concentricity of the elements is improved, as compared to prior art systems wherein elements of a seal assembly are machined independently and then assembled.
An improved high pressure fluid seal assembly has been shown and described. From the foregoing, it will be appreciated that, although specific embodiments of the invention have been described herein for purposes of illustration, various modifications may be made without deviating from the spirit of the invention.
1 S Thus, the present invention is not limited to the embodiments described herein, but rather as defined by the claims which follow.
A bushing 50 positioned within the high pressure region 23 houses a spring 52 which engages the annular seal 17 and urges it toward the first annular groove 15 to substantially prevent the annular seal from moving out of the first annular groove. The annular seal 17 has a flange portion 54 which engages the spring 52 and substantially prevents the spring from moving laterally into contact with the plunger 14.
The seal carrier 12 also has an integral, annular guidance bearing 19, which is positioned in a second annular groove 16 within the bore 13. As seen in Figure 3, the second annular groove 16 and guidance bearing 19 positioned therein are axially spaced from the first annular groove 15 and annular seal 17 contained therein.
The inner diameter 20 of the guidance bearing 19 is smaller than the inner diameter 21 of the seal carrier bore 13 in a region 11 between the seal 17 and guidance bearing 19. For example, in a preferred embodiment, the inner diameter 20 is .0005-.0015 inch smaller than the inner diameter 21. In this manner, the end region 18 of annular seal 17 is supported by region 11 of the seal carrier 12; however, region 11 of seal carrier 12 is not in contact with the plunger 14, given the configuration of the guidance bearing 19.
A seal assembly provided in accordance with a preferred embodiment of the present invention therefore supports a seal directly by the seal carrier, eliminating the need for a back-up ring. The integral guidance bearing prevents the plunger from contacting the seal carrier, thereby reducing the frictional heating in the vicinity of the seal, which in turn extends the life of the seal. To further increase the longevity of the assembly, the materials for the components are selected to minimize the friction between the plunger and the guidance bearing and between the plunger and the seal. In a preferred embodiment, the plunger 14 is made of partially stabilized zirconia ceramic, the guidance bearing 19 is made of a resin impregnated graphite, and the seal 17 is made of an ultra-high molecular weight polyethylene. However, it should be noted that a variety of materials may be used, and the selection of the materials for the components are interdependent.
To further increase the reliability of the seal, the seal assembly is preferably manufactured by pressing the guidance bearing 19 into the seal carrier 12, and machining the bore through the guidance bearing and through region 11 of the seal carrier in the same machining setup. As discussed above, the inner diameter of the bore in region 11 is machined slightly larger than the inner diameter 20 of the bore through the guidance bearing. However, by machining both areas in the same setup, the concentricity of the elements is improved, as compared to prior art systems wherein elements of a seal assembly are machined independently and then assembled.
An improved high pressure fluid seal assembly has been shown and described. From the foregoing, it will be appreciated that, although specific embodiments of the invention have been described herein for purposes of illustration, various modifications may be made without deviating from the spirit of the invention.
1 S Thus, the present invention is not limited to the embodiments described herein, but rather as defined by the claims which follow.
Claims (7)
1. ~A high pressure fluid seal assembly comprising:
a seal carrier (12) having a bore (13) through which a reciprocating plunger (14) may pass, and having a first annular groove (15) concentric with the bore (13) and a second annular groove (16) that is concentric with the bore (13) and that is axially spaced from the first annular groove;
an annular seal (17) positioned in the first annular groove (15) and facing the plunger (14) an end region (18) of the seal (17) being supported by the seal carrier (12); and an annular guidance bearing (19) positioned in the second annular groove (16) to contact the plunger (14), an inner diameter (20) of the annular guidance bearing (19) being from about 0 0127 mm (0 0005) to about 0 0381 mm (0.0015 inch) smaller than an inner diameter (21) of the bore (13) of the seal carrier (12) in a region (11) between the first annular groove (15) and the second annular groove (16).
a seal carrier (12) having a bore (13) through which a reciprocating plunger (14) may pass, and having a first annular groove (15) concentric with the bore (13) and a second annular groove (16) that is concentric with the bore (13) and that is axially spaced from the first annular groove;
an annular seal (17) positioned in the first annular groove (15) and facing the plunger (14) an end region (18) of the seal (17) being supported by the seal carrier (12); and an annular guidance bearing (19) positioned in the second annular groove (16) to contact the plunger (14), an inner diameter (20) of the annular guidance bearing (19) being from about 0 0127 mm (0 0005) to about 0 0381 mm (0.0015 inch) smaller than an inner diameter (21) of the bore (13) of the seal carrier (12) in a region (11) between the first annular groove (15) and the second annular groove (16).
2. ~A high pressure fluid seal carrier (12) comprising:
a body having a bore (13) through which a reciprocating plunger (14) may pass, and having an annular groove (15) concentric with the bore (13) adapted to receive an annular seal (17), the seal carrier (12) being provided with an annular guidance bearing (19) that is concentric with the bore (13) to contact the plunger (14) and is axially spaced from the annular groove (15), the inner circumference of the annular guidance bearing (19) forming a portion of the bore (13) through which the reciprocating plunger (14) may pass, an inner diameter (20) of the annular guidance bearing (19) being from about 0.0127 mm (0.0005 inch) to about 0,0381 mm (0.0015 inch) smaller than an inner diameter (21) of the bore (13) of the seal carrier (12) in the region (11) between the annular groove (15) and the annular guidance bearing (19).
a body having a bore (13) through which a reciprocating plunger (14) may pass, and having an annular groove (15) concentric with the bore (13) adapted to receive an annular seal (17), the seal carrier (12) being provided with an annular guidance bearing (19) that is concentric with the bore (13) to contact the plunger (14) and is axially spaced from the annular groove (15), the inner circumference of the annular guidance bearing (19) forming a portion of the bore (13) through which the reciprocating plunger (14) may pass, an inner diameter (20) of the annular guidance bearing (19) being from about 0.0127 mm (0.0005 inch) to about 0,0381 mm (0.0015 inch) smaller than an inner diameter (21) of the bore (13) of the seal carrier (12) in the region (11) between the annular groove (15) and the annular guidance bearing (19).
3. A high pressure pump assembly comprising:
a plunger (14) coupled to a drive mechanism (26), the plunger (14) reciprocating in a high pressure chamber (23) formed in a high pressure cylinder (24), and a seal assembly provided adjacent to the high pressure chamber (23) to substantially prevent the leakage of high pressure fluid from the high pressure chamber (23), the seal assembly having a bore (13) through which the reciprocating plunger (14) passes, and having a first annular groove (15) concentric with the bore (13) and a second annular groove (16) that is axially spaced from the first annular groove (15) and that is concentric with the bore (13), an annular seal (17) being positioned in the first annular groove (15), an end region (18) of the seal (17) being supported by the seal carrier (12), and an annular guidance bearing (19) positioned in the second annular groove (16) to contact the plunger (14), an inner diameter (20) of the annular guidance bearing (19) being from about 0,0127 mm (0.0005 inch) to about 0,0381 mm (0.0015 inch) smaller than an inner diameter (21) of the bore (13) of the seal carrier (12) in the region (18) between the first annular groove (15) and the second annular groove (16) such that the plunger (14) is in contact with the guidance bearing (19), but is not in contact with the seal carrier (12).
a plunger (14) coupled to a drive mechanism (26), the plunger (14) reciprocating in a high pressure chamber (23) formed in a high pressure cylinder (24), and a seal assembly provided adjacent to the high pressure chamber (23) to substantially prevent the leakage of high pressure fluid from the high pressure chamber (23), the seal assembly having a bore (13) through which the reciprocating plunger (14) passes, and having a first annular groove (15) concentric with the bore (13) and a second annular groove (16) that is axially spaced from the first annular groove (15) and that is concentric with the bore (13), an annular seal (17) being positioned in the first annular groove (15), an end region (18) of the seal (17) being supported by the seal carrier (12), and an annular guidance bearing (19) positioned in the second annular groove (16) to contact the plunger (14), an inner diameter (20) of the annular guidance bearing (19) being from about 0,0127 mm (0.0005 inch) to about 0,0381 mm (0.0015 inch) smaller than an inner diameter (21) of the bore (13) of the seal carrier (12) in the region (18) between the first annular groove (15) and the second annular groove (16) such that the plunger (14) is in contact with the guidance bearing (19), but is not in contact with the seal carrier (12).
4. The assembly according to claim 3, further comprising an elastomeric seat (25) positioned around an outer circumference of the annular seal (17) to energize the annular seal (17) during the start of a pressure stroke.
5. The assembly according to claim 3 wherein the materials of the annular guidance bearing (19), the plunger (14) and the seal (17) are selected to ensure that a low coefficient of friction exists between the plunger (14) and the seal (17) and between the plunger (14) and the guidance bearing (19).
6. The apparatus according to claim 5 wherein the plunger (14) is made of partially stabilized zirconia ceramic, the guidance bearing (19) is made of resin impregnated graphite, and the seal (17) is made of an ultra-high molecular weight polyethylene.
7. A method for making a high pressure fluid seal comprising:
inserting an annular guidance bearing (19) into an opening (13) of a seal carrier (12), and machining a bore (13) in the guidance bearing (19) and in the seal carrier (12) during the same setup, an inner diameter (20) of the bore (13) through the guidance bearing (19) being from about 0.0127 mm (0.0005 inch) to about 0.0381 mm (0.0015 inch) smaller than an inner diameter (21) of the bore through the seal carrier (12).
inserting an annular guidance bearing (19) into an opening (13) of a seal carrier (12), and machining a bore (13) in the guidance bearing (19) and in the seal carrier (12) during the same setup, an inner diameter (20) of the bore (13) through the guidance bearing (19) being from about 0.0127 mm (0.0005 inch) to about 0.0381 mm (0.0015 inch) smaller than an inner diameter (21) of the bore through the seal carrier (12).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US08/932,690 US6086070A (en) | 1997-09-18 | 1997-09-18 | High pressure fluid seal assembly |
| US932,690 | 1997-09-18 | ||
| PCT/US1998/019517 WO1999014501A1 (en) | 1997-09-18 | 1998-09-17 | Plunger seal assembly for a high pressure pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2303100A1 CA2303100A1 (en) | 1999-03-25 |
| CA2303100C true CA2303100C (en) | 2003-12-02 |
Family
ID=25462738
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002303100A Expired - Fee Related CA2303100C (en) | 1997-09-18 | 1998-09-17 | Plunger seal assembly for a high pressure pump |
Country Status (10)
| Country | Link |
|---|---|
| US (2) | US6086070A (en) |
| EP (1) | EP1015767B1 (en) |
| JP (1) | JP4416317B2 (en) |
| AT (1) | ATE239172T1 (en) |
| AU (1) | AU9398598A (en) |
| CA (1) | CA2303100C (en) |
| DE (1) | DE69814111T2 (en) |
| ES (1) | ES2198752T3 (en) |
| TW (1) | TW428068B (en) |
| WO (1) | WO1999014501A1 (en) |
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| US7247006B2 (en) * | 2002-01-02 | 2007-07-24 | Flow International Corporation | Method and apparatus for sealing an ultrahigh-pressure fluid system |
| USD561877S1 (en) | 2002-01-02 | 2008-02-12 | Flow International Corporation | Seal carrier for ultrahigh-pressure fluid systems |
| US7568424B2 (en) * | 2002-01-02 | 2009-08-04 | Flow International Corporation | Method and apparatus for sealing an ultrahigh-pressure fluid system |
| US6918595B2 (en) | 2002-11-22 | 2005-07-19 | Dionex Corporation | Seal for high-pressure pumping system |
| US20040256811A1 (en) * | 2002-11-22 | 2004-12-23 | Proper George N. | Seal for high-pressure pumping system |
| US7908934B2 (en) * | 2008-02-29 | 2011-03-22 | Dionex Corporation | Valve assembly |
| DE102008055124A1 (en) * | 2008-12-23 | 2010-07-01 | Robert Bosch Gmbh | Seal for at least one electrical line |
| US8502074B2 (en) * | 2010-11-23 | 2013-08-06 | Matcor, Inc. | Seal for anode connection to cable and method of use |
| CN103403412B (en) | 2011-03-10 | 2016-08-24 | 沃特世科技公司 | Seal assemblies for reciprocating and rotating applications |
| KR101297846B1 (en) * | 2011-04-25 | 2013-08-19 | 최인수 | The plunger seal of plunger pump for high pressure homogenizer |
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| WO2013109474A1 (en) | 2012-01-19 | 2013-07-25 | Flow International Corporation | Devices for sealing high pressure and ultrahigh pressure fluid systems |
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| KR20190034342A (en) * | 2016-08-15 | 2019-04-01 | 하이퍼썸, 인크. | Detection of fluid leaks in pressurized systems of water jet cutting systems |
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| EP4165328A4 (en) | 2020-06-11 | 2024-06-05 | Quantum Servo Pumping Technologies Pty Ltd | HIGH PRESSURE SEALS |
| JP7586430B2 (en) * | 2021-06-23 | 2024-11-19 | 株式会社丸山製作所 | Reciprocating Pump |
| CN113266548B (en) * | 2021-07-19 | 2021-10-08 | 山东高原油气装备有限公司 | A hydraulic bidirectional mud pump for preventing clogging in oil exploitation |
| CN116857370B (en) * | 2023-07-24 | 2026-03-17 | 燕山大学 | Sealing and isolation devices with media differences |
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| US3776558A (en) * | 1972-03-17 | 1973-12-04 | Exxon Production Research Co | Tandem packing for a reciprocating pump |
| CA1077731A (en) * | 1976-02-25 | 1980-05-20 | Robert R. Bell | Drive rod coupling for positive displacement pump |
| US4101099A (en) * | 1977-09-15 | 1978-07-18 | The United States Of America As Represented By The Secretary Of The Navy | Repeatable release holdback bar |
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| JP2862615B2 (en) * | 1989-04-04 | 1999-03-03 | フロー インターナショナル コーポレーション | Seal assembly |
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| US5593166A (en) * | 1994-03-02 | 1997-01-14 | Fisher Controls International, Inc. | Low friction packing |
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| US5493954A (en) * | 1994-11-18 | 1996-02-27 | Flow International Corporation | Self-venting seal assembly |
| JP3390290B2 (en) * | 1995-06-21 | 2003-03-24 | カヤバ工業株式会社 | How to assemble the hydraulic cylinder |
| JP3781463B2 (en) * | 1995-11-10 | 2006-05-31 | 株式会社ニクニ | mechanical seal |
| US5692851A (en) * | 1996-10-07 | 1997-12-02 | Pace; Paul G. | Elongated member connector |
| JPH10299925A (en) * | 1997-04-23 | 1998-11-13 | Zexel Corp | Pressure control valve |
-
1997
- 1997-09-18 US US08/932,690 patent/US6086070A/en not_active Expired - Lifetime
-
1998
- 1998-05-01 US US09/071,706 patent/US6145845A/en not_active Expired - Lifetime
- 1998-09-17 CA CA002303100A patent/CA2303100C/en not_active Expired - Fee Related
- 1998-09-17 ES ES98947136T patent/ES2198752T3/en not_active Expired - Lifetime
- 1998-09-17 AU AU93985/98A patent/AU9398598A/en not_active Abandoned
- 1998-09-17 AT AT98947136T patent/ATE239172T1/en not_active IP Right Cessation
- 1998-09-17 JP JP2000512009A patent/JP4416317B2/en not_active Expired - Lifetime
- 1998-09-17 WO PCT/US1998/019517 patent/WO1999014501A1/en not_active Ceased
- 1998-09-17 EP EP98947136A patent/EP1015767B1/en not_active Expired - Lifetime
- 1998-09-17 DE DE69814111T patent/DE69814111T2/en not_active Expired - Fee Related
- 1998-09-18 TW TW087115583A patent/TW428068B/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| EP1015767A1 (en) | 2000-07-05 |
| DE69814111D1 (en) | 2003-06-05 |
| US6086070A (en) | 2000-07-11 |
| JP4416317B2 (en) | 2010-02-17 |
| TW428068B (en) | 2001-04-01 |
| JP2001516847A (en) | 2001-10-02 |
| EP1015767B1 (en) | 2003-05-02 |
| WO1999014501A1 (en) | 1999-03-25 |
| ES2198752T3 (en) | 2004-02-01 |
| US6145845A (en) | 2000-11-14 |
| CA2303100A1 (en) | 1999-03-25 |
| ATE239172T1 (en) | 2003-05-15 |
| DE69814111T2 (en) | 2004-03-18 |
| AU9398598A (en) | 1999-04-05 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |